Quick change bearing holder apparatus for a rotating shaft

ABSTRACT

A quick change bearing holder apparatus for a rotating shaft including a shaft housing, a conical bearing holder and a bearing retainer element. The shaft housing has a conical socket. The conical bearing holder has an outer conical surface compatible with the conical socket of the shaft housing. The bearing retainer element mounts to the shaft housing to urge the bearing holder into the conical socket of the shaft housing. Lubrication feed lines and openings and drain lines and openings may be included in the shaft housing and conical bearing holder. Lubrication may further be facilitated using circumferential grooves in the shaft housing or the conical bearing holder. The outer conical surface of the conical bearing holder may have a taper angle that forms a self ejecting taper.

CROSS-REFERENCE TO RELATED APPLICATIONS

The present application is a continuation of U.S. application Ser. No.12/565,041 entitled “WATERCRAFT PROPELLER PROPULSION SYSTEM HAVING AGIMBAL ASSEMBLY WITH AN EXTERNAL GIMBAL RING” by same inventor, issuingOct. 8, 2013 as U.S. Pat. No. 8,550,863, which itself claims the benefitof U.S. Provisional Application Ser. No. 61/099,820, filed on Sep. 24,2008, which are both herein incorporated by reference for all intentsand purposes.

BACKGROUND OF THE INVENTION

1. Field of the Invention

The present invention relates to watercraft, and more particularly to aquick change bearing holder apparatus for a rotating shaft.

2. Description of the Related Art

Various types of propulsion systems are known for watercraft. Thepresent disclosure relates to screw propeller propulsion units thatmount to a transom of a boat and are often referred to as “surfacepiercing drives” or “surface drives”. Surface drive propeller propulsionsystems are typically provided on boats which operate at high speed andusually have a partially submerged propeller with at least one degree ofarticulation for tilt or steering adjustment. Conventional surface drivepropulsion systems for boats commonly have a rotating propeller shaftcoupled via a rotating Universal joint (U joint) to the drive shaft of aboat motor or engine. The drive shaft, propeller shaft and Universaljoint are housed within a non-rotating housing with an articulationjoint that allows the drive system to have at least one degree ofarticulation for tilt or steering adjustment. Various types ofarticulation joints are known, such as a gimbal. Some conventionalconfigurations do not use a gimbal, but rather use a ball or hollowsphere fitted into a hemispherical seat. The present disclosure,however, is directed towards a gimbal or gimbal assembly.

It is noted that the gimbal, although similar in appearance to aUniversal joint, has entirely different function, stress analysis, anddesign constraints such that it warrants a different art classification.A Universal joint is a device used to transmit rotary power in the formof torque from a first rotating shaft to a second rotating shaft at ahigh rate of speed in which one shaft is allowed to move through variousangular deflections relative to the other shaft. A gimbal, on the otherhand, is a non-rotating device that is often used to house a Universaljoint contained within to provide a guide to the Universal joint and totransmit axial load as common with conventional propeller propulsionsystems.

A gimbal assembly includes three main components including a firstgimbal end, a gimbal ring, and a second gimbal end. The first gimbal endis hingedly connected to the gimbal ring by a pair of gimbal pins toallow articulation about a first axis. The second gimbal end is alsoconnected to the gimbal ring by a second pair of gimbal pins to allowarticulation about a second axis. One conventional gimbal assemblyincludes a gimbal ring that is internal to one gimbal end and that isexternal to the other gimbal end. Another configuration includes agimbal ring that is internal to both gimbal ends. Conventionalpropulsion units use standard rolling element bearings pressed onto thepropeller shaft and bolted into the propeller shaft housing and aredifficult to access and remove and/or replace. Conventional drivesystems do not have a means to measure propeller thrust forces.

BRIEF DESCRIPTION OF THE DRAWINGS

The benefits, features, and advantages of the present invention willbecome better understood with regard to the following description, andaccompanying drawings, in which:

FIG. 1 is an exploded view of the components between Match Line C-C andMatch Line D-D of FIG. 2, depicting a gimbal assembly including a firstgimbal end, a gimbal ring, and a second gimbal end.

FIG. 2 is a simplified and exploded view of the sequential relationshipof adjacent elements of a watercraft propeller propulsion system havingan articulation joint configured as a gimbal assembly with an externalgimbal ring according to an exemplary embodiment as further detailed inremaining FIGS. 1, 3 and 37.

FIG. 3 is a phantom drawing of the gimbal assembly and shows a zigzagshaped gimbal ring in the center.

FIG. 4 is combination of an exploded view and a phantom view of thedrive shaft housing located between Match Line D-D and Match Line E-E ofFIG. 2.

FIG. 5 is a combination of an exploded view and shows a portion of thedrive shaft housing located between Match Line E-E and Match Line F-F ofFIG. 2.

FIG. 6 is a combination of an exploded view and a phantom view of thepropeller shaft housing and enclosed propeller shaft located betweenMatch Line C-C and Match Line B-B of FIG. 2.

FIG. 7 is a combination of an exploded view and a phantom view of thethrust bearing can and enclosed propeller shaft located between MatchLine B-B and Match Line A-A of FIG. 2.

FIG. 8 is a simplified drawing of a conventional Universal joint thatcouples a drive shaft as shown on the right to a propeller shaft asshown on the left.

FIG. 9 is an end view of a bearing retainer plate located inside of thegimbal assembly and is used to secure a bearing holder in place insideof the shaft housing that protrudes into the gimbal end.

FIG. 10 is an end view of a seal retainer plate used inside of thegimbal assembly to secure a shaft seal in place.

FIG. 11 is a side view of the bearing retainer plate of FIG. 9 and theseal retainer plate of FIG. 10 and includes the clamping bolts to retainthe plates.

FIG. 12 is a side sectional view of FIG. 11 but rotated 90 degrees toshow the relation of the drive shaft 422, or alternately, propellershaft 522, and the bearing holder 622 and the shaft seal 625 andrespective retaining plates. This view is a mirror image of FIG. 11 asit represents the similar items but as located on the other end of thegimbal assembly.

FIG. 13 shows a side view of a retaining bolt that holds the gimbalassembly to either the drive shaft housing to the propeller shafthousing.

FIG. 14 shows a side view of the thrust collar that is connected to thedrive shaft of FIG. 5.

FIG. 15 is an end view of the thrust collar of FIG. 14 as mounted on thedrive shaft.

FIG. 16 is an end view of the oil drain ring of FIG. 5.

FIG. 17 is an end view of the drive shaft input seal retainer plate ofFIG. 5.

FIG. 18 is perspective view of the drive shaft input seal retainer plateof FIG. 17.

FIG. 19 is perspective view of the drive shaft forward thrust plate andbolts of FIG. 5.

FIG. 20 is perspective view of the drive shaft rearward thrust plate andbolts of FIG. 5.

FIG. 21 is perspective view of the drive shaft forward bearing holderretainer plate and bolts of FIG. 5.

FIG. 22 is an end view of the drive shaft rearward thrust bearing plateof FIGS. 5 and 20.

FIG. 23 is an end view of the drive shaft forward thrust bearing plateand bolts of FIGS. 5 and 21.

FIG. 24 is an enlarged sectional view of the propeller shaft annularthrust piston and propeller shaft annular thrust cylinder of FIG. 7.

FIG. 25 is a side view of the thrust bearing containment can of FIG. 7.

FIG. 26 is an end view of the thrust bearing containment can of FIG. 25.

FIG. 27 is a side view of propeller shaft rear bearing holder retainerplate of FIG. 7.

FIG. 28 is an end view of propeller shaft rear bearing holder retainerplate of FIG. 27.

FIG. 29 is a side view of propeller shaft rear seal retaining plate ofFIG. 7.

FIG. 30 is an end view of propeller shaft rear seal retaining plate ofFIG. 29.

FIG. 31 is an exploded assembly drawing shown as a perspective view ofthe bearing housing and seal parts at the rearward end of the propellershaft as shown in FIGS. 25-30 that are part of the bearing housing andseal of FIG. 7.

FIG. 32 is an enlarged sectional view of the bearing holder in relationto the drive shaft and the drive shaft housing of FIG. 4.

FIG. 33 is an end sectional view of the bearing holder and drive shafthousing as taken along Section Line 33-33 of FIG. 32.

FIG. 34 is another view of FIG. 32 of a bearing holder fitted into adrive shaft housing including O-ring grooves and O-rings.

FIG. 35 is a view of a ball bearing held in bearing holder of FIG. 32.

FIG. 36 is a view of a tapered roller bearing held in bearing holder ofFIG. 32.

FIG. 37 is a 360 degree view of the gimbal assembly of FIG. 1 showingthe cylindrical parts as though they were cut open and unwrapped to layflat on a sheet of paper to illustrate the construction of the parts.

DETAILED DESCRIPTION

The following description is presented to enable one of ordinary skillin the art to make and use the present invention as provided within thecontext of a particular application and its requirements. Variousmodifications to the preferred embodiment will, however, be apparent toone skilled in the art, and the general principles defined herein may beapplied to other embodiments. Therefore, the present invention is notintended to be limited to the particular embodiments shown and describedherein, but is to be accorded the widest scope consistent with theprinciples and novel features herein disclosed.

A watercraft propeller propulsion system as described herein issignificantly more user friendly than conventional watercraft propellerpropulsion systems. One embodiment relates to the construction of agimbal assembly that connects the propeller shaft housing to the driveshaft housing that is connected to the boat. One embodiment relates tothe quick-change journal bearing holders to support the propeller shaft.One embodiment relates to a thrust bearing assembly that is also used tomeasure propeller thrust forces. One embodiment relates to a bearingassembly with a lubricant impelling system and method.

The various embodiments provide any of one or more benefits as describedherein. One benefit is that the propulsion unit may be designed to bemore accessible for ease of maintenance of internal parts, and can beserviced with simpler tools. Another benefit is that the gimbal assemblyuses an external gimbal ring, which permits ease of maintenance to theUniversal joint located within, while still maintaining compact overallassembly dimensions. Another benefit is that the gimbal ring is designedin a zigzag configuration to permit the gimbal pins to be easilyremovable and installable. In one embodiment, for example, gimbal pinsare clamped to the external gimbal ring using U bolts and correspondingnuts which are more easily accessible and removable with a singlewrench. For example, the U bolt nuts may be loosened and tightenedwithout a backup wrench. Also, the U bolt avoids a blind or threadedhole in the gimbal ring as is common for conventional gimbal assemblies.A zigzag shaped configuration allows the most compact gimbal ringbecause the clearance between the gimbal ring and the gimbal ends can beminimized since the area where the gimbal ring overlaps the gimbal endis at the same area where the two parts swivel parallel to each other. Acompact gimbal ring has a smaller diameter than a conventional gimbalring which allows the propeller shaft and drive shaft to be located aslow as possible at the transom of a boat. Such configuration enables thepropeller thrust vector to have a minimum vertical component, so thatthe thrust vector is more parallel to the direction of travel of theboat as compared to conventional gimbal assemblies which are larger andless compact. Furthermore, in conventional gimbal assemblyconfigurations, a bellows is mounted around the Universal joint insidethe larger conventional gimbal assembly to minimize exposure of theUniversal joint to water, sand and other contaminants. A gimbal assemblywith an external gimbal ring facilitates a more compact configuration sothat the bellows may be mounted outside of the external gimbal ring.This enables quick change of the bellows without disassembly of thegimbal.

Another benefit is that the bearings that support the rotating shaft maybe held in tapered holders for quick change from the stationary housing.This quick-change can be done by using simple hand tools. Anotherbenefit is that the bearings may be configured with positive oil feedfrom a pressurized source for circulating cooled and filtered oilthrough the bearings. Another benefit is that the thrust load from thepropeller may be constrained and transferred to the propeller shafthousing by a hydraulic or hydrostatic bearing that uses a pressurizedoil source to levitate the thrust ring of the propeller shaft on acontained reservoir of oil to allow the frictional forces to beminimized. Another benefit is that the hydrostatic thrust bearing may beused as part of a remotely readable measure of the amount of thrustpushing the boat through the water at any given operating condition orspeed. Alternately, the hydrostatic thrust bearing can be locked againstrotation and used as a non-rotating load cell used for measuring axialload forces. Another benefit is to provide bearing assembly with an oilimpelling means to circulate oil lubricant.

FIG. 2 is a simplified and exploded view of the sequential relationshipof adjacent elements of a watercraft propeller propulsion system havingan articulation joint configured as a gimbal assembly with an externalgimbal ring according to an exemplary embodiment as further detailed inremaining FIGS. 1, 3 and 37. FIG. 2 is a guide to the spatialrelationship of adjacent elements of the total assembly, in which thepropeller is shown on the left, the gimbal assembly is shown in themiddle as a blank space, and the power input end is shown on the rightand connects to a motor (not shown). Each figure includes Match Linesthat delineate the sequential element from its neighboring element asthe viewer goes from one end of the boat propulsion unit to the oppositeend of the boat propulsion unit. The sequence of elements is shown inFIG. 2 and shows the propeller on the left end of the figure near MatchLine A-A, and shows the power input end at the right end of the figurenear Match Line F-F. The two sections located on the left side betweenMatch Line A-A and Match Line C-C depict the propeller shaft end of thesystem. The two sections located on the right side between Match LineD-D and Match Line F-F depict the drive shaft end of the system. Themotor for the boat is connected at Match Line F-F. Match Lines may nothave any structural meaning and may simply represent a convenient pointon a larger detailed drawing where the components seem to end, but it issimply for convenience and clarity that the Match Lines are shown at thelocations selected. The concept of an “exploded view” is used to depictthe individual elements in relation to the adjacent elements and iscommonly used in machine design and assembly drawing. The forward end ofthe boat propulsion unit is towards Match Line F-F where the motor islocated, and the rearward end of the boat propulsion unit is towardsMatch Line A-A where the propeller is located.

FIG. 1 is an exploded view of the components between Match Line C-C andMatch Line D-D of FIG. 2 and depicts a gimbal assembly including a firstgenerally cylindrical gimbal end, a gimbal ring, and a second generallycylindrical gimbal end. This assembly allows the propeller shaft housinglocated to the left of Match Line C-C to articulate relative to thedrive shaft housing located to the right of Match Line D-D. The gimbalassembly is a non-rotating assembly that goes over the rotatingUniversal joint contained within, but not shown in this figure. Referalso to FIG. 3 and FIG. 37.

The gimbal assembly has a novel arrangement of a gimbal ring 344 that islocated externally to both gimbal ends. Gimbal assemblies are usuallyconstructed from two end elements referred hereinafter as gimbal ends,plus a gimbal ring, and two pairs of gimbal pins. Conventional gimbalassemblies are constructed with the gimbal ring fitting in the radialspace between the two gimbal ends. That is to say, in a conventionalconfiguration, the gimbal ring is located both radially internal of onegimbal end and radially external of the other gimbal end, so that it isnot an external gimbal ring. The gimbal ring 344 described herein isexternal since it is located radially external of both the first gimbalend 354 and located radially external of the second gimbal end 364.Thus, the gimbal assembly includes a first gimbal end 354, and a gimbalring 344, and a second gimbal end 364, wherein said gimbal ring islocated radially external to both the first gimbal end and locatedradially external to the second gimbal end.

FIG. 1 also shows another novel aspect in which the gimbal ring 344 isoffset in a zigzag fashion such that the four individual gimbal pins 345are located near the longitudinal faces of the gimbal ring wherein theadjacent gimbal pins, that are located 90 degrees away from each other,are near opposite longitudinal end faces, a first end face 396, and asecond end face 397, of the gimbal ring, yet are aligned to be locatedon a single transverse plane. The plane of the gimbal pins is orientedto be transverse and perpendicular to the longitudinal axis of thegimbal assembly. External gimbal ring 344 is a generally cylindricalelement and has ends that resemble a zigzag shape. The zigzag isintentional to allow the gimbal pins 345 to be mounted to the alternatefaces of the gimbal ring at corresponding recesses 346 and secured withU-bolts 355 and nuts 356. This is a face loaded gimbal ring. That is tosay, in one embodiment the gimbal assembly includes a gimbal ring 344 inwhich the gimbal ring is generally cylindrical and has two pairs ofgimbal pins 345 such that a first pair of gimbal pins are locateddiametrically opposite of each other on the gimbal ring, so that asecond pair of gimbal pins are located diametrically opposite of eachother on the same gimbal ring, and so that the first pair of gimbal pinsform a first line and the second pair of gimbal pins from a second lineand wherein the first line and second line intersect and form a plane inwhich the plane is generally transverse to the longitudinal axis of thegimbal ring, and in which the first pair of gimbal pins is located at afirst longitudinal end face of the gimbal ring and the second pair ofgimbal pins is located at a second longitudinal end face of the gimbalring. The shape of the gimbal ring according to one embodiment isfurther explained in FIG. 37.

A first advantage to this zigzag ring configuration is that the gimbalpins can be placed in a common transverse plane relative to thecenterline of the propulsion unit and the gimbal ring diameter can beminimized. This reduced diameter is possible because each transverseaxis of the gimbal ring pivots about each opposite pair of gimbal pins345 on opposite sides of a first gimbal end 354 and on opposite sides ofa second gimbal end 364, in closer clearance than would be possible witha gimbal ring that was symmetric about the common transverse plane ofthe gimbal pins. Thus, this is a space saving feature to allow a morecompact overall diameter of the gimbal assembly. This is desirable inthis application on boats because it is desirable to minimize theoverall diameter of the gimbal assembly.

A second advantage to the zigzag configuration is that the radialclearance between the gimbal ring 344 and a gimbal end 354 is minimizedto therefore minimize the bending moments on the gimbal pins 345 andalso minimize the internal torsional stresses generated in the gimbalring.

A third advantage to this zigzag shaped gimbal ring 344 is that thegimbal pins 345 can be secured to the faces of the gimbal ring withU-bolts 355 and nuts 356 to facilitate the ease of removal andreplacement of the gimbal pins. The U-bolts and nuts are simply loosenedand the gimbal pins are pulled out or reinserted to allow disassemblyand reassembly of the gimbal assembly. Gimbal cross pins 348 preventinserting the gimbal pins 345 too deeply into the grip of the U bolts355. This disassembly and reassembly of the gimbal unit is beneficial togain access for removal and replacement of the rotating Universal joint602 that is located inside the gimbal assembly. An exemplary Universaljoint is shown in FIG. 8.

The term zigzag is used to figuratively describe the shape of the endfaces of the gimbal ring 344 as can be seen clearly in FIG. 37. The endfaces are undulated along the axis of the gimbal assembly and have twohigh and two low areas on each end face of the gimbal ring and arephased such that the general length of the gimbal ring is relativelyuniform. Each end face of the gimbal ring is undulated with two highsand two lows per side.

The first gimbal end 354 is generally a cylinder shape and has two axialextensions commonly referred in the industry as first end yoke 398 thatincludes a pair of gimbal pin holes 349 to receive gimbal pins 345.Similarly, the second gimbal end 364 is generally a cylinder shape andhas two axial extensions common in the industry shown as second end yoke399 that includes a pair of gimbal pin holes 349 to receive gimbal pins345. This arrangement is further explained in FIG. 37.

FIG. 3 is a phantom drawing of the gimbal assembly and shows a zigzagshaped gimbal ring 344 in the center and includes the gimbal pins 345.In one embodiment, the gimbal ring appears as a zig-zag shaped cylinder.The figure also shows the corrugated bellows 375 on the outside to sealout water. The splined shaft 523 shown on the left is the input end ofthe propeller shaft and the splined shaft 423 shown on the right is theconnecting end of the drive shaft. Not shown in this view is a rotatingUniversal joint that connects the spline of the rotating drive shaft tothe spline of the rotating propeller shaft.

FIG. 3 is similar to FIG. 1 but is more detailed to show adjacent partsof the boat propulsion system. FIG. 3 is not an exploded diagram, but isgenerally a longitudinal section view along the centerline of the driveshaft spline 423 shown on the right side and the propeller shaft spline523 shown on the left side. Drive shaft spline 423 is held in radialposition relative to the gimbal assembly by the use of journal bearingsmounted in a cone shaped bearing holder 622 having a defined angle oftaper. The bearing holder is held into a mating tapered hole by abearing retainer plate 623 and by retainer bolts 626 and nuts 356. Shaftseal 625 is located outside of the bearing retainer plate by sealretainer plate 624 that is, in turn, clamped in position by boltssimilar to retaining bolts 626. A first gimbal end 354 is integral witha first gimbal flange 384. The gimbal flange is typically circular andhas bolt holes around the perimeter to accommodate bolting to thetransom of the boat at Match Line DD. Other methods of fastening arecontemplated. A second gimbal end 364 is likewise integral with a secondgimbal flange 394. The first gimbal end and first gimbal flange aregenerally identical to the second end, but are rotated 90 degreesrelative to each other. Shaft splines 423 or 523, bearing mounting andshaft sealing details of the drive shaft 422 and propeller shaft 522within the gimbal assembly are very similar on either end. These detailsare shown and described in greater clarity in FIGS. 9-12. Alignment pins311 are inserted temporarily into alignment pin holes 312 in firstgimbal end 354 and second gimbal end 364 to keep the ends from floppingaround when the gimbal assembly is being reassembled. Gimbal pin 345 haspull ring 347 and gimbal pin cross pin 348 that limits the insertiondepth of the gimbal pin into the U bolt 355. Bellows 375 is clamped tobellows ring 374 with bellows clamp 376. Bellows ring has fill and drainholes 377 to flush and purge the enclosed space. Gimbal ends have accessholes 366, inspection holes 365, and grease fittings 325 to pump sealantinto the cracks between mating components.

FIG. 4 is combination of an exploded view and a phantom view of thedrive shaft housing 424 located between Match Line D-D and Match LineE-E of FIG. 2. This portion of the propulsions unit is located where thedrive shaft penetrates the transom 112 of the boat. The drive shafthousing flange 410 is integral with the drive shaft housing 424. This isthe portion of the propulsion system that pierces the transom 112 of theboat from the outside and is bolted in place by transom plate 417,transom bolts 415, and nuts 356. The drive shaft 422 is located insidethe center bore of the drive shaft housing 424 and is carried on ajournal bearing mounted inside bearing holder 622 located on either endof the drive shaft housing 424. Oil feed inlet 409 on the drive shafthousing provides a convenient point for introducing lubricating oil intoan internally drilled longitudinal oil feed line 411. Pressurized oilfeeds in both directions to lubricate the bearings on either end of thedrive shaft. Oil is returned via a similar internally drilled oil drainline 413 and drains out of the drive shaft housing via oil drain outlet412 into a contained area defined by rubber reduction sleeve 495 and oildrain ring 490 and secured with hose clamps 376 including other oilcontainment parts in the adjacent portion of the drive shaft housing asshown in FIG. 5. U bolts 431 are shown separate from the housing butactually go into the crescent cuts 421 and are used to hold the adjacentparts in place in the drive shaft housing. The bellows 375 of FIG. 3 areheld in place with hose clamps 376.

FIG. 5 is a combination of an exploded view and shows a portion of thedrive shaft housing located between Match Line E-E and Match Line F-F asnoted in FIG. 2. This portion of the propulsion system is located wherethe drive shaft connects to the inboard style boat engine or motor notshown, but located to the right side of the drawing.

FIG. 5 shows a continuation of FIG. 4 between Match Lines E-E and MatchLines F-F and is shown as the input end of the drive shaft 422 where thedrive shaft connects to the boat motor (not shown) via drive shaft inputspline 499 on the right end of the drive shaft. The drive shaft ishollow and has a threaded rod 472 running down the center to theopposite end used to hold the Universal joint in place on the oppositeend of the drive shaft. A drive shaft nut 471 with O-ring 473, istightened to pull the Universal joint tight onto the drive shaft outputspline 423 shown in FIG. 3. Section Line 17-17 refers to FIG. 17 whereit is seen that the entire assembly is generally cylindrical. Chains 445and screen door style spring 447 are tensioned and looped over andattach to bolts 439 to urge motor end seal retaining plate 438 to theleft to secure shaft seal 625 against drive shaft forward thrust plate482 to form a compression seal. Anti-rattle sleeves 448 are short piecesof loose fitting rubber hose slid onto the chain to prevent chainrattle. The shaft seal may be configured as a simple sheet of Teflonwith a slightly undersized hole through the center to slip over thedrive shaft. The Teflon seal is conformal and lends itself to quick andeasy field repairs.

U bolts 433, 435, and eyebolt 437 are shown at the top and bottom ofFIG. 5 to illustrate how these appear when properly installed adjacentto the drive shaft 422 in this figure. Bearing holder 622 is urged tothe left by drive shaft forward bearing retainer plate 432 and heldtight by U bolts 431 of FIG. 4. Bearing retainer plate 432 now providesan anchor point for U bolts 433 that is used to adjustably secure driveshaft rearward thrust plate 434 in correct axial position. U bolts 435are secured to drive shaft rearward thrust plate 434 and bridge over thegap to a similar drive shaft forward thrust plate 482 discussed earlier.The drive shaft thrust bearing collar 440 is secured to the drive shaftand rides between a pair of drive shaft thrust bearing blocks 436 oneither side of the thrust collar. Tie wires 443 hold thrust bearingblocks in place. The drive shaft thrust collar is detailed in FIG. 14and in FIG. 15. This thrust bearing assembly can be designed as a lightweight assembly because only the inertial mass of the drive shaft andthe Universal joint are carried by this assembly and none of thepropeller thrust is carried here.

Lubricating oil is contained by rubber sleeve 496 and rubber sleeve 497that are both secured to drive shaft oil drain ring 490 by using hoseclamps 476. The rubber sleeves are generally short pieces of largediameter hose.

Although other bolting and sealing methods may be used, it is desired tohave a very field serviceable unit that can be repaired and adjustedusing the simplest of hand tools and using captive bolts that swingaside after loosening the nuts, and U bolts to eliminate the need for asecond wrench to hold the other end of the bolt, or to have blind orthreaded holes in the drive shaft housing.

FIG. 6 is a combination of an exploded view and a phantom view of thepropeller shaft housing 524 and enclosed propeller shaft 522 locatedbetween Match Line C-C and Match Line B-B of FIG. 2. FIG. 6 is a sideview similar to the others and shows a propeller shaft housing 524between Match Line B-B and Match Line C-C as seen in FIG. 2. This end issimilar to the drive shaft end of the propulsion system in that thepropeller shaft housing is generally cylindrical with a hollow centerand a propeller shaft 522 running down through the center. The rotatingpropeller shaft is carried by a journal bearing in a bearing holder 622on each end of the propeller shaft. Lubricant input hole 510 feedscleaned and cooled oil to the bearings in the bearing holders. Oil isfed via oil feed tube 511. Oil drained out of the rearward bearingreturns via the annular space between the propeller shaft and thepropeller shaft housing and combines with oil in oil drain line 509 toultimately exit via oil drain hole 512.

Spring levers 549 with spring 547 and cable hook 548 exert a tensionforce on tension cable 545 to urge shaft seal 625 into place as shown onFIG. 7. Crescent cuts 521 provide a place to secure U bolts 531 to thepropeller shaft housing in a fashion similar to that shown on the driveshaft end as shown in FIG. 4 and FIG. 5. Oil inlet hole 512 feeds oilvia oil lines 514 to the thrust bearing assembly of FIG. 7. Propellershaft housing flange 510 is integral to propeller shaft housing 524 andfurther stiffened by braces 525. U-bolt 313 are held in place by coverstrips 524, sealed by patch seals 527, and all held in place by screwclamps 526.

FIG. 7 is a combination of an exploded view and a phantom view of thethrust bearing can 534 and enclosed propeller shaft 522 located betweenMatch Line B-B and Match Line A-A as noted in FIG. 2. A propeller 111 isshown to the left of Match Line A-A. FIG. 7 is similar to FIG. 5 in thatit has a shaft bearing in bearing holder 622, a thrust bearing assemblydiscussed below, and a shaft seal between the propeller shaft 522 andthe thrust bearing containment can 534. The propeller 111 slides ontopropeller shaft spline 599.

The thrust bearing assembly is much heavier on the propeller shaft thanit is on the drive shaft because the entire thrust load from thepropeller is carried in this assembly and is transferred to thepropeller shaft housing 524 and ultimately through the gimbal assemblyand to the boat hull at the transom. The thrust bearing assembly iscomprised of an enlarged portion of the propeller shaft against whichforward thrust collar 580 and rearward thrust collar 550 are abutted.The forward thrust collar 580 has impeller holes 581 drilled radially,plus others, to act as the impeller of a small oil pump to induce oilflow through the forward thrust bearing assembly located just to theright of the forward thrust collar. The forward thrust bearing assemblyhas a plurality of thrust bearing elements 557 located between aplurality of thrust bearing races 559. The thrust bearing elements maybe anti friction rolling elements or may be low friction Teflon washers.The thrust bearing assembly also has an annular thrust cylinder 537 andannular thrust piston 535 shown in an enlarged view in FIG. 24. Theannular thrust cylinder is circular in shape and forms an annular spacebetween the inner wall and outer wall of the thrust cylinder. In otherwords, the thrust cylinder looks like a square sided “U” shape that isrotated about the centerline of the propeller shaft. The annular thrustpiston is circular in shape similar to a fat and thick washer and fitsinto the circular groove of the annular thrust cylinder. The annularthrust piston has at least one oil feed passage 505 drilled through itfrom front to rear. This oil feed passage allows high pressure oil toflow from a source forward of the annular thrust piston to thepressurized chamber formed behind the annular thrust piston and withinthe annular thrust cylinder. There is at least one bleed port 507located near the rear portion of the inside wall of the annular thrustcylinder wherein the bleed port allows excess oil to flow out of theconfined space between the head of the annular thrust piston and thebottom of the annular thrust cylinder. The annular thrust cylinderrotates along with the propeller shaft. The annular thrust piston isstationary relative to the propeller shaft housing.

This annular thrust piston and annular thrust cylinder serve twopurposes. The first purpose is to provide a hydrostatic oil cushionbetween a rotating part, e.g., the annular thrust cylinder, and astationary part, e.g., the annular thrust piston. The roles of these twocomponents can be reversed. Thus, the combination forms a very lowfriction thrust bearing assembly. The second purpose is to provide athrust force measuring system that is based on the prevailing oilpressure within the confined space of the annular thrust cylinder andannular thrust piston. An oil pump with a high pressure discharge islocated at some convenient location on the boat. Somewhere on thedischarge line of the pump is a metering orifice. Downstream of themetering orifice is located an oil pressure gauge and an oil line routedback to feed the metered oil to the oil feed passage through the thrustpiston. As the thrust force of the propeller pushes the propeller shaftand annular thrust cylinder forward, the bleed port in the annularthrust cylinder is progressively covered more and more by the forwardmotion and the oil pressure builds to a higher and higher value becausethe bleed port is progressively covered more and more. Thus, the oilpressure gauge reads a progressively higher pressure proportionate tothe thrust force of the propeller on the boat. The converse operation,wherein the propeller generates less and less thrust, allows the annularthrust cylinder to move rearward relative to the annular thrust pistonand tends to uncover the bleed port in the annular thrust cylinder wall,hence, the pressure on the oil pressure gauge is decreased proportionateto the decrease in the thrust force of the propeller on the boat. Inthis embodiment, metered oil is fed through a passage in bearing holder622 and into the forward face of the annular thrust piston 535. Othermeans of oil feed can be used Annular thrust piston and annular thrustcylinder can be replaced with electronic load cells of similar annularshape, for example, “Large I.D. Through Hole Load Cell LC8213-200-5K”sold by Omega Engineering.

Rearward thrust collar 550 and rearward thrust bearings 536 push againstthrust bearing containment can 534 when the propeller generates rearwardthrust. Rear thrust bearings can be needle type or Teflon washersincluding shims for axial position adjustments.

Thrust bearing containment can 534 is in the shape of a cylinder with afull diameter hole at one end and an axial hole in the other end wherethe propeller shaft 522 exits. U bolts 533 and nuts 356 hold the thrustbearing containment can tight against bearing retainer plate 532.Bearing retainer plate is held in place against the propeller shafthousing by U bolts 531 and nuts 356.

Shaft seal 625 can be a sheet of Teflon with a tight fit over thepropeller shaft 522 and is held tight against the rear face of thethrust bearing containment can 534 by means of rear propeller shaft sealholder plate 538 and is urged forward by tension cables 545 and cablehooks 548 shown in FIG. 6. Rear propeller shaft seal holder plate 538has string cutters 560 with sharp edges to cut any fishing line woundaround the propeller shaft. String cutters are also known as linecutters. Cable grommets 539 prevent chafing of tension cables 545 andpreserve rotational alignment.

The propeller 111 is mounted to the propeller shaft in the ordinary wayby use of propeller shaft splines 599. Forward motion of the propelleris limited by a propeller thrust washer 710 that has an internallytapered shoulder and fits on a complimentary tapered shoulder near theend of the propeller shaft 522. Propeller thrust washer 710 has rotatingstring cutters 712 with sharp edges to cut any fishing line wound aroundthe propeller shaft. String cutters are also known as line cutters.

FIG. 8 is a simplified drawing of a conventional Universal joint 602that couples a drive shaft 422 as shown on the right to a propellershaft 522 as shown on the left. The universal joint is located withinthe confines of the gimbal assembly of FIG. 1 and FIG. 3. Theillustrated Universal joint 602 is market available and typical of adouble yoke Cardan style. These Universal joints are also referred to as“three piece Universal joints” comprising an input section 642, a centersection 672, and an output section 652. Not shown, but common to allthese Universal joints is a cross piece that is inserted into bearingholes 662 in each of the three sections. The Universal joint is locatedinside of the gimbal assembly of FIG. 1 and FIG. 3, but is not shown inthose views to prevent clutter. The input section 642 is connected todrive shaft spline 423 and the output section 652 is connected to thepropeller shaft spline 523 with a sliding fit. Universal joint centersection 672 is located between the input section and the output section.The input section is secured to the drive shaft by a bolt 472 and washer402 to prevent axial motion between the drive shaft and the inputsection. The drive shaft thrust bearing assembly of FIG. 5 is adjustedto correctly locate the Universal joint center section to belongitudinally centered within the gimbal assembly of FIG. 1 and FIG. 3.That is to say, the center plane of the Universal joint center section672 is longitudinally centered at the same plane as the gimbal pins 345of the gimbal assembly of FIG. 1 and FIG. 3. Slight longitudinaldisplacement can be tolerated, but it is not desirable.

FIG. 9 is an end view of a bearing retainer plate 623 located inside ofthe gimbal assembly and is used to secure a bearing holder in placeinside of the shaft housing that protrudes into the gimbal end. Thebearing retainer plate 623 is viewed along Section Line 9-9 of FIG. 3.Second gimbal end 364, or alternately, first gimbal end 354, are shownas cross hatched and access holes 366 allow access to bolts and nutsinside. Slots at the top and bottom of the bearing retainer plate arefor U bolts 626 shown in FIG. 11.

FIG. 10 is an end view of seal retainer plate 624 as viewed alongSection Line 10-10 of FIG. 3, in which the seal retainer plate usedinside of the gimbal assembly to secure a shaft seal in place. Secondgimbal end 364, or alternately, first gimbal end 354, are shown as crosshatched and access holes 366 allow access to bolts and nuts inside.Slots at the top and bottom of the seal retainer plate are for receivingswing bolts 627 shown in FIG. 11.

FIG. 11 is a side view of the bearing retainer plate of FIG. 9 and theseal retainer plate of FIG. 10 and includes the clamping bolts to retainthe plates. FIG. 11 is a top view of an enlarged portion of FIG. 3 asviewed along Section Line 11-11. This view straddles Match Line C-C andshows how the U bolt 626 secures the bearing retainer plate 623 withnuts 356. Also shown is the seal retainer plate 624 held in place byswing bolt 627 and nut 356. The swing bolt is configured as an eye boltfitted onto the square U bolt 626 and both are inserted into gimbalplate 394 or (384) before it is bolted to propeller shaft housing plate510 or (drive shaft housing plate 410). This construction of usingcaptive bolts allows both the U bolt and the swing bolt to be tightenedor loosened with a single wrench and swung aside for removal of therespective retainer plates without loosing either the nuts or the bolts.

FIG. 12 is a side view of FIG. 11 and is taken along Section Line 12-12of FIG. 3, but is rotated 90 degrees to show the relation of the driveshaft 422, or alternately, propeller shaft 522, and the bearing holder622 and the shaft seal 625 and respective retaining plates. This view isa mirror image of FIG. 11 as it represents the similar items but aslocated on the other end of the gimbal assembly. This view shows how thebearing retainer plate 623 holds the bearing holder 622 into place inthe drive shaft housing 424, or alternately in the propeller shafthousing 524. Shaft seal 625 is held by shaft seal retainer plate 624.Bearing retainer plate 623 is held in position by U bolts 626 and nuts356 that can be loosened and swung away for removal of the bearingholder. Shaft seal retainer plate 624 is held in place by eye bolt 627and nuts 356 that can be loosened and swung away for removal of theshaft seal 625.

FIG. 13 shows a side view of a retaining bolt 313 that holds the gimbalassembly to either the drive shaft housing, or alternatively, to thepropeller shaft housing. FIG. 13 is a view of clamping U bolt 313 andnuts 310 that hold second gimbal flange 394, or alternately first gimbalflange 384, together against propeller shaft housing flange 510 or driveshaft housing flange 410 as seen in FIG. 3 and FIG. 6, or FIG. 3 andFIG. 4, respectively.

FIG. 14 is a side view of drive shaft thrust collar 440 mounted on driveshaft 422 as viewed in FIG. 5. Drive shaft thrust collar takes on theappearance of a V belt pulley with flat faces and has the small diameterof the pulley groove cut away at two locations to allow the buckleportion of a pair of collar clamps 480 to intrude into a groove cut intothe drive shaft. Thus, the thrust collar is easily removed and replacedwithout any loose part by simply loosening the collar clamps to slidethe drive shaft thrust collar off the end of the drive shaft. Anordinary hose clamp can be used as a collar clamp. However, a pair ofhose clamps connected nose to tail to each other is better because itensures symmetry such that rotating balance is preserved.

FIG. 15 is an end view of the thrust collar 440 as mounted on the driveshaft 422 of FIG. 14 taken along Section Line 15-15 and shows the detailof the buckle portion of the collar clamps 480 actually intruding intothe groove in drive shaft 422.

FIG. 16 is an end view of oil drain ring 490 as shown in Section Line16-16 of FIG. 4 and similarly in FIG. 5. Oil drain ring is made of rigidmaterial, usually metal, that has drain holes 492 for hose fitting toreturn oil to a reservoir not shown. Hose clamps 376 hold hose 496 andhose 497, as shown in FIG. 5, in place to prevent leakage.

FIG. 17 is an end view of drive shaft oil seal retainer ring 438 asviewed in Section Line 17-17 of FIG. 5. Bolts 439 are secured with nuts356 and provide an attachment point for chain 445 used to tension driveshaft oil seal retainer plate against shaft seal 625 shown in FIG. 5.

FIG. 18 is a perspective view of drive shaft oil seal retainer ring 438shown in FIG. 17 and FIG. 5. Bolts 439, with nuts 356, provide anattachment point for chain.

FIG. 19 is a perspective view of drive shaft forward thrust plate 482 asshown in FIG. 5. Location for U bolts 435, eye bolts 437, and nuts 356are shown.

FIG. 20 is a perspective view of drive shaft rearward thrust bearingplate 434 as shown in FIG. 5. Locations for U bolts 433, and nuts 356,are shown.

FIG. 21 is a perspective view of drive shaft forward end bearingretainer plate 432 as shown in FIG. 5. Locations for U bolts 431, andnuts 356, are shown.

FIG. 22 is an end view of drive shaft rearward thrust bearing plate 434as shown in FIG. 5 and FIG. 20 but is shown to illustrate theapproximate layout required for machining of the bolt holes and slots.

FIG. 23 is an end view of drive shaft forward bearing retainer plate 432as shown in FIG. 5 and FIG. 21 but is shown to illustrate theapproximate layout required for machining of the bolt holes and slots.

FIG. 24 is an enlarged and detailed side sectional view of an annularthrust cylinder 537 and an annular thrust piston 535 as seen in FIG. 7on propeller shaft 522. Details of the oil bleed port 507 through theannular thrust cylinder and oil feed passage 505 drilled through annularthrust piston are shown. This is configured as an annular piston thatfits inside an annular cylinder that are filled from a high pressure oilsource through the oil feed passages to cause the oil to push theannular cylinder towards the rearward position and away from the annularpiston. Propeller thrust forces in the forward direction cause theannular cylinder to be pushed forward towards the annular piston. As thepropeller thrust forward forces increase, the oil bleed port isprogressively closed by the closing motion of the annular piston intothe annular cylinder, thus raising the oil pressure as read by theremote gauge. Thus, the trapped oil causes the annular piston to assumean equilibrium position in the annular cylinder. As the propeller thrustdecreases, the annular cylinder moves rearward by a small amount thusallowing more of the trapped oil to flow out of the oil bleed port andthe system comes to a new equilibrium position. The pressure of the oiltrapped in the cylinder is proportional to the forward thrust force ofthe propeller. This pressure is read by a remote gauge located at thedrivers convenience to monitor the propeller thrust. This combination ofan annular cylinder and an annular piston also serve as a hydraulicbearing that is a hydrostatic bearing. This is different from ahydrodynamic bearing such as a Kingsbury thrust bearing or a journalsleeve bearing which operate by a skiing action of a moving shaftagainst a stationary bearing causing the oil to be swept into a thinwedge shaped film of oil separating the two mating machine parts. One ofthe embodiments of this invention is the oil filled annular cylinderwith an annular piston that serve either as a hydraulic thrust bearing,or as a hydraulic thrust force sensor.

FIG. 25 is a side view of thrust bearing containment can 534 as shown inFIG. 7. This figure also shows details of an oil return hole 570 asdrilled diagonally into a threaded hole 572 for an oil drain fittingthat is piped back to an oil reservoir on the boat.

FIG. 26 is an end view of thrust bearing containment can 534 as shown inFIG. 25 as viewed along Section Line 26-26. Various holes are shown forU bolts 533 and tension cables 545 shown in FIG. 31. Oil return hole 570and threaded hole 572 of FIG. 25 are shown.

FIG. 27 is a side view of propeller shaft rear bearing retainer plate532 as shown in FIG. 7.

FIG. 28 is an end view of propeller shaft rear bearing retainer plate532 as shown in FIG. 27 as viewed along Section Line 28-28. Holes forbolts and slots for cables are shown for machining layout.

FIG. 29 is a side view of propeller shaft seal retainer plate 538 asshown in FIG. 7. Tension cable 545 is shown passing through cablegrommets 539 and includes sharp edged string cutters 560. String cuttersare also called line cutters.

FIG. 30 is an end view of propeller shaft seal retainer plate 538 asshown in Section Line 30-30 in FIG. 29. Cable grommets 539 and sharpedged string cutters 560 are also shown. String cutters are also calledline cutters.

FIG. 31 is a perspective of an exploded view of the propeller shaftthrust containment can 534 including U bolts 531, and U bolts 533, andnuts 356 that holds the propeller shaft thrust containment can againstpropeller shaft bearing retainer plate 532 which is in turn held againstbearing holder 622 forced into the propeller shaft housing 524, bothshown in FIG. 7 by U bolts 531. Also shown is propeller shaft sealretainer plate 538 with string cutters 560 and cable grommets 539 thathold it in place around the propeller shaft by means of tension cables545. All of which can be seen in FIG. 7.

FIG. 32 is a side sectional view of bearing holder 622 as seen in FIG. 3near Match Line D-D. Drive shaft housing 424 has a tapered seat toreceive the tapered outside diameter of the bearing holder. Oil supplydrilled hole 411, shown in FIG. 4, supplies pressurized oil from aremote oil reservoir not shown. Oil return drilled hole 413 provides adrain path away from the bearing as seen in FIG. 4. Oil supply drilledhole communicates with a first circumferential groove 931 that allowsthe bearing holder to be inserted in any angular orientation and stillensure that oil will feed into bearing holder oil feed passage 911 intoan internal annular groove 951 to feed lubricating oil into sleevebearings 922. Similarly, oil return drilled hole 413 aligns with asecond circumferential groove 933 that allows the lubricating oil thatseeps out of the end of the sleeve bearings to slide down into facegroove 953 and pass through drilled drain holes 913 and to oil returndrilled hole 413 to ultimately return to a reservoir located on theboat. Bearing holder 622 has a recessed face area 952 to allow clearancefor the return oil to flow radially from the drive shaft outward toannular face groove 953. As stated before, bearing retainer plate 623urges bearing holder 622 into the mating taper hole of the drive shafthousing 424. The location of the shaft seal 625 is shown.Circumferential O-ring grooves 944 are located on the tapered side andon the end face of the bearing holder 622. Drive shaft housing has aninside bore diameter 963 greater than the diameter of the shaft 422 withsufficient clearance for a drain path 965 for excess oil. The insidediameter of the bearing 922 is the point where the shaft is in contactwith the bearing. The slope of the taper angle 420 is greater than thecritical self-ejecting taper angle as determined from machinery designhandbooks. Taper angle 420 is a self ejecting taper such that thetangent of the taper angle is greater than the coefficient of frictionbetween the two mating materials. The bearing holder has a taper angle420 that is generally equal to the mating angle of the drive shafthousing 424. The same is true for the propeller shaft housing 524.

FIG. 33 is an end view of FIG. 32 as taken along Section Line 33-33. Oilsupply drilled hole 411 and oil return drilled hole 413 are shown indrive shaft housing 424. Sleeve bearing 922 supports drive shaft 422.The inside of the drive shaft housing 424 has an inside bore diameter963 greater than the drive shaft 422. The inside diameter of the shaftbearing 922 is the point where the shaft is in contact with the bearing.

FIG. 34 is a side sectional view of bearing holder 622 similar to FIG.32. Alternate embodiments of the oil supply channels and oil drainchannels include circumferential supply grooves 932 and circumferentialdrain grooves 934 to be cut into the drive shaft housing 424. Otherfeatures of bearing holder 622 remain the same. Resilient O-rings 945are placed in the circumferential O-ring grooves 944.

FIG. 35 shows an alternate style of bearings common in the industry thusmounted in bearing holder 622. Ball bearing 923 is held in place by thebearing retainer plate 623. The inner race is commonly secured to therotating drive shaft 422 by set screws or press fit as common in machinepractice. Mounting and retaining these bearings is common knowledge.Other features of the bearing holder and shaft housing are the same asFIG. 32. Taper angle 620 of the bearing holder is equal to the taperangle 420 of the shaft housing.

FIG. 36 shows an alternate style of bearings common in the industry thusmounted in bearing holder 622. Tapered roller bearing 924 is held inplace by the bearing retainer plate 623. The inner race is commonlysecured to the rotating drive shaft 422 by set screws or press fit ascommon in machine practice. Mounting and retaining these bearings iscommon knowledge. Other features of the bearing holder and shaft housingare the same as FIG. 32.

All of the above described features in FIG. 32, FIG. 33, FIG. 34, FIG.35, and FIG. 36 also apply to the bearing holder of the propeller shafthousing 524. Although the tapered section is generated from a singlegeometric cone, it is contemplated to use multiple geometric cones toaccommodate other design constraints. The single geometric cone isusually sufficient and is the easiest to manufacture.

FIG. 37 is a view of FIG. 1, but shows what the cylindrically shapedgimbal assembly would look like if it was cut open and laid out flat ona sheet of paper. This view emphasizes the zigzag nature of the gimbalring 344 showing how the gimbal pins 345 are mounted to the face of thegimbal ring by use of U bolts 355 and nuts 356. Gimbal pins form acommon flat plane transverse to the axis of the gimbal assembly. This isa face loaded gimbal ring. Although it is possible to axially offset onepair of gimbal pins relative to the other pair of gimbal pins, there isno real advantage and it is poor machine design practice because it willcause improper operation of the Universal joint contained within thegimbal assembly similar to that caused by improper axial alignment.Improper axial alignment causes excessive vibration and wear. The gimbalring 344 has a first ring edge 396 facing towards a first gimbal end354. The gimbal ring has a second ring edge 397 facing towards a secondgimbal end 364. Both the first ring edge and the second ring edge aregenerally parallel to each other and have a zigzag shape that isundulated from one gimbal pin 345 to the next gimbal pin. However, thegimbal pins are arranged to form a single transverse plane across thegimbal ring. The first gimbal end 354 has a pair of first end gimbalyokes 398 that are longitudinal extensions of the cylindrical form ofthe first gimbal end. These gimbal yokes have holes located on oppositesides of the cylindrical form to receive gimbal pins 345. The secondgimbal end 364 has a pair of second end gimbal yokes 399 that arelongitudinal extensions of the cylindrical form of the second gimbalend. These gimbal yokes have holes located on opposite sides of thecylindrical form to receive gimbal pins 345. In this layout, gimbal ring344 appears longer than first gimbal end 354 or second gimbal end 364.That is to be expected because the gimbal ring has a larger diameter,hence a larger circumference, than first gimbal end or second gimbalend. The gimbal pins are separable from the gimbal yokes.

Although the present invention has been described in considerable detailwith reference to certain preferred versions thereof, other versions andvariations are possible and contemplated. Those skilled in the artshould appreciate that they can readily use the disclosed conception andspecific embodiments as a basis for designing or modifying otherstructures for carrying out the same purposes of the present inventionwithout departing from the spirit and scope of the invention as definedby the appended claims.

1. A quick change bearing holder apparatus for a rotating shaft,comprising: a shaft housing for the rotating shaft, wherein said shafthousing has a conical socket; a conical bearing holder having an outerconical surface compatible with said conical socket of said shafthousing; and a bearing retainer element that mounts to said shafthousing to urge said conical bearing holder into said conical socket. 2.The quick change bearing holder apparatus of claim 1, wherein: saidshaft housing further comprises at least one lubrication supply line andsupply line opening in said conical socket; and wherein said conicalbearing holder further comprises at least one feed passage aligned withsaid supply line opening of said shaft housing.
 3. The quick changebearing holder apparatus of claim 2, wherein said shaft housing furthercomprises at least one circumferential groove aligned with said supplyline opening of said conical socket.
 4. The quick change bearing holderapparatus of claim 2, wherein said conical bearing holder comprises acircumferential groove aligned with said supply line opening of saidconical socket.
 5. The quick change bearing holder apparatus of claim 4,wherein said conical bearing holder has at least one feed line alignedwith said circumferential groove.
 6. The quick change bearing holderapparatus of claim 2, wherein said conical bearing holder comprises aplurality of circumferential grooves.
 7. The quick change bearing holderapparatus of claim 1, wherein: said shaft housing further comprises atleast one lubrication return line and return line opening in saidconical socket; and wherein said conical bearing holder furthercomprises at least one drain passage aligned with said return lineopening of said shaft housing.
 8. The quick change bearing holderapparatus of claim 7, wherein said shaft housing further comprises atleast one circumferential groove aligned with said return line openingof said conical socket.
 9. The quick change bearing holder apparatus ofclaim 7, wherein said conical bearing holder comprises a circumferentialgroove aligned with said drain line opening of said conical socket. 10.The quick change bearing holder apparatus of claim 9, wherein saidconical bearing holder has at least one drain line aligned with saidcircumferential groove.
 11. The quick change bearing holder apparatus ofclaim 1, wherein said conical bearing holder further comprises at leastone circumferential O-ring groove.
 12. The quick change bearing holderapparatus of claim 1, wherein said conical bearing holder furthercomprises a self ejecting taper.
 13. A quick change bearing holderapparatus for a rotating shaft, comprising: a shaft housing for arotating shaft, wherein said shaft housing has a conical socket; aconical bearing holder having an outer conical surface compatible withsaid conical socket of said shaft housing, wherein said outer conicalsurface has a taper angle that forms a self ejecting taper; and abearing retainer element for mounting to said shaft housing to urge saidconical bearing holder into said conical socket.
 14. The quick changebearing holder apparatus of claim 13, wherein: said shaft housingfurther comprises at least one lubrication supply line and supply lineopening in said conical socket; and wherein said conical bearing holderfurther comprises at least one feed passage aligned with said supplyline opening of said shaft housing.
 15. The quick change bearing holderapparatus of claim 14, wherein said shaft housing further comprises atleast one circumferential groove aligned with said supply line openingof said conical socket.
 16. The quick change bearing holder apparatus ofclaim 14, wherein said conical bearing holder comprises acircumferential groove aligned with said supply line opening of saidconical socket.
 17. The quick change bearing holder apparatus of claim16, wherein said conical bearing holder has at least one feed linealigned with said circumferential groove.
 18. The quick change bearingholder apparatus of claim 14, wherein said conical bearing holdercomprises a plurality of circumferential grooves.
 19. The quick changebearing holder apparatus of claim 13, wherein: said shaft housingfurther comprises at least one lubrication return line and return lineopening in said conical socket; and wherein said conical bearing holderfurther comprises at least one drain passage aligned with said returnline opening of said shaft housing.
 20. The quick change bearing holderapparatus of claim 19, wherein said shaft housing further comprises atleast one circumferential groove aligned with said return line openingof said conical socket.
 21. The quick change bearing holder apparatus ofclaim 19, wherein said conical bearing holder comprises acircumferential groove aligned with said drain line opening of saidconical socket.
 22. The quick change bearing holder apparatus of claim21, wherein said conical bearing holder has at least one drain linealigned with said circumferential groove.